JPS6216335B2 - - Google Patents
Info
- Publication number
- JPS6216335B2 JPS6216335B2 JP58122980A JP12298083A JPS6216335B2 JP S6216335 B2 JPS6216335 B2 JP S6216335B2 JP 58122980 A JP58122980 A JP 58122980A JP 12298083 A JP12298083 A JP 12298083A JP S6216335 B2 JPS6216335 B2 JP S6216335B2
- Authority
- JP
- Japan
- Prior art keywords
- suspension member
- vibration
- mass
- vehicle
- outer cylinder
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000000725 suspension Substances 0.000 claims description 55
- 239000012212 insulator Substances 0.000 description 18
- 230000000694 effects Effects 0.000 description 8
- 238000006073 displacement reaction Methods 0.000 description 5
- 238000010521 absorption reaction Methods 0.000 description 4
- 230000003139 buffering effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 239000000853 adhesive Substances 0.000 description 2
- 230000001070 adhesive effect Effects 0.000 description 2
- 238000005452 bending Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000004073 vulcanization Methods 0.000 description 2
- 230000008094 contradictory effect Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/22—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper characterised by comprising also a dynamic damper
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G99/00—Subject matter not provided for in other groups of this subclass
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
- F16F1/38—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
- F16F1/387—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type comprising means for modifying the rigidity in particular directions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
- F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
- F16F7/108—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on plastics springs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/20—Type of damper
- B60G2202/25—Dynamic damper
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
- B60G2204/10—Mounting of suspension elements
- B60G2204/15—Mounting of subframes
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
- B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
- B60G2204/41—Elastic mounts, e.g. bushings
- B60G2204/4104—Bushings having modified rigidity in particular directions
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
- B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
- B60G2204/41—Elastic mounts, e.g. bushings
- B60G2204/4104—Bushings having modified rigidity in particular directions
- B60G2204/41042—Bushings having modified rigidity in particular directions by using internal cam surfaces
Description
【発明の詳細な説明】
産業上の利用分野
本発明はサスペンシヨンメンバを車体に緩衝機
能をもつて結合するようにした筒状弾性ブツシユ
に関する。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a cylindrical elastic bushing for coupling a suspension member to a vehicle body with a damping function.
従来の技術
一般に、自動車は車体が懸架装置に懸架される
ようになつているが、該懸架装置のサスペンシヨ
ンメンバは筒状弾性ブツシユを介して前記車体に
結合されるようになつている。たとえば、前記懸
架装置は日産自動車株式会社発行のサービス周報
(昭和54年11月第401号)第98頁にセミトレーリン
グアーム式のものが示されている。この懸架装置
は車輪を支持する一対のサスペンシヨンアームが
上下揺動可能にサスペンシヨンメンバに取着され
ており、かつ、該サスペンシヨンメンバは車両左
右方向に延びており、このサスペンシヨンメンバ
の両端部を筒状弾性ブツシユとしてのマウントイ
ンシユレータを介して車体側に装着してある。該
マウントインシユレータは同心状に設けられる内
筒、外筒およびこれら内、外筒を連結するゴム製
の主弾性体を備えており、外筒がサスペンシヨン
メンバ側、内筒がこの内筒に挿通される取付ボル
トを介して車体側に装着されるようになつてい
る。そして、車両走行時、前記サスペンシヨンメ
ンバにはパワートレイン系の振動とか路面から車
輪が受ける振動がサスペンシヨンアームを介して
伝達され、該サスペンシヨンメンバの振動が、前
記主弾性体の緩衝機能によつて車体側に伝達され
るのを抑制するようにしてある。2. Description of the Related Art In general, the body of an automobile is suspended by a suspension system, and the suspension member of the suspension system is connected to the vehicle body via a cylindrical elastic bush. For example, a semi-trailing arm suspension system is shown on page 98 of Service Bulletin (No. 401, November 1972) published by Nissan Motor Co., Ltd. In this suspension system, a pair of suspension arms that support wheels are attached to a suspension member so as to be able to swing up and down, and the suspension member extends in the left-right direction of the vehicle. The part is attached to the vehicle body via a mount insulator as a cylindrical elastic bush. The mount insulator includes an inner cylinder, an outer cylinder, and a main elastic body made of rubber that connects these inner and outer cylinders, with the outer cylinder facing the suspension member and the inner cylinder facing the inner cylinder. It is designed to be attached to the vehicle body via a mounting bolt that is inserted into the body. When the vehicle is running, vibrations from the power train system and vibrations received by the wheels from the road surface are transmitted to the suspension member via the suspension arm, and the vibrations of the suspension member are transferred to the buffering function of the main elastic body. Therefore, it is designed to suppress transmission to the vehicle body side.
しかしながら、前記マウントインシユレータの
主弾性体は緩衝機能を行なうのみではなく、サス
ペンシヨンメンバの変位を規制するストツパーと
しての機能をも行なう必要がある。このため、主
弾性体で互いに相反する緩衝機能およびストツパ
ー機能の両者を同時に満足することは不可能で、
どうしてもある振動周波数帯の振動が車体側に伝
達され、特にパワートレイン系の低周波の上下振
動が入力されて室内こもり音の原因になつてしま
うという問題点があつた。そのためにサスペンシ
ヨンメンバの端部に別体のダイナミツクダンパを
装着したものが提案された。(ニツサンサービス
周報419号昭和55年6月発行参照)しかしながら
別体のダイナミツクダンパを装着するものは部品
点数が多くコストが嵩むと共に、大型化してしま
うという問題点があつた。 However, the main elastic body of the mount insulator must not only perform a buffering function, but also function as a stopper for regulating displacement of the suspension member. For this reason, it is impossible for the main elastic body to simultaneously satisfy both the buffering function and the stopper function, which are contradictory to each other.
The problem was that vibrations in a certain vibration frequency band were inevitably transmitted to the vehicle body, and in particular, low-frequency vertical vibrations from the powertrain system were input, causing muffled noise in the room. For this purpose, it has been proposed to install a separate dynamic damper at the end of the suspension member. (Refer to Nitsusan Service Bulletin No. 419, June 1980) However, models equipped with a separate dynamic damper had the problem that they had many parts, increased costs, and were larger.
本発明はかかる従来の問題点に鑑みて、筒状弾
性ブツシユにダイナミツクダンパ機能を与えるこ
とにより、従来の筒状弾性ブツシユでは抑制しき
れなかつた周波数帯の振動がサスペンシヨンメン
バ側から車体側に伝達されるのを、サスペンシヨ
ンの大型化を伴うことなく、かつ低コストをもつ
て防止するようにした筒状弾性ブツシユを提供す
ることを目的とする。 In view of these conventional problems, the present invention provides a cylindrical elastic bushing with a dynamic damper function, thereby allowing vibrations in frequency bands that could not be suppressed by the conventional cylindrical elastic bushings to be transferred from the suspension member side to the vehicle body side. It is an object of the present invention to provide a cylindrical elastic bushing which prevents the transmission of air to the surrounding area without increasing the size of the suspension and at low cost.
問題点を解決するための手段
本発明はかかる目的を達成するために、車体側
に装着される内筒、サスペンシヨンメンバ側に装
着される外筒およびこれら内、外筒を連結する主
弾性体からなり、前記サスペンシヨンメンバを車
体に支持させるようにしたサスペンシヨンメンバ
の筒状弾性ブツシユにおいて、前記外筒をサスペ
ンシヨンメンバの端部に配置すると共に、該外筒
の内側に、車両上下方向に剪断変形する副弾性体
を介してダイナミツクダンパ機能を行なうに十分
な質量を有する質量体を装着することにより構成
してある。Means for Solving the Problems In order to achieve the above object, the present invention has an inner cylinder mounted on the vehicle body side, an outer cylinder mounted on the suspension member side, and a main elastic body connecting these inner and outer cylinders. In the cylindrical elastic bushing of the suspension member, the suspension member is supported by the vehicle body, and the outer cylinder is disposed at an end of the suspension member, and the outer cylinder is provided inside the outer cylinder in the vertical direction of the vehicle. It is constructed by mounting a mass body having a mass sufficient to perform a dynamic damper function via an auxiliary elastic body that undergoes shear deformation.
作 用
以上の構成により本発明のサスペンシヨンメン
バの筒状弾性ブツシユにあつては、サスペンシヨ
ンメンバから外筒に上下振動が入力されると、こ
の振動は副弾性体を介して質量体に伝達される。
このとき、該質量体と前記外筒との間には副弾性
体によつて振動の位相が180゜ずれることにな
り、ここにダイナミツクダンパが構成される。ま
た、前記副弾性体はパワートレイン系の振動方向
である車両上下方向に剪断変形されるようになつ
ているので、副弾性体を大きくすることなく前記
振動方向には前記副弾性体のばね定数を小さくし
て、ダイナミツクダンパの共振周波数を特に室内
こもり音の原因となるパワートレイン系の低周波
の上下振動周波数にチユーニングすることができ
る。更に、前記外筒つまり筒状弾性ブツシユがサ
スペンシヨンメンバの端部に設けられることによ
り、振動低減の更なる向上が図られることにな
る。Effect With the above configuration, in the cylindrical elastic bush of the suspension member of the present invention, when vertical vibration is input from the suspension member to the outer cylinder, this vibration is transmitted to the mass body via the auxiliary elastic body. be done.
At this time, the phase of vibration is shifted by 180° between the mass body and the outer cylinder due to the auxiliary elastic body, thereby forming a dynamic damper. Furthermore, since the secondary elastic body is designed to be sheared in the vertical direction of the vehicle, which is the vibration direction of the power train system, the spring constant of the secondary elastic body can be adjusted in the vibration direction without increasing the size of the secondary elastic body. can be made smaller, and the resonant frequency of the dynamic damper can be tuned to the low-frequency vertical vibration frequency of the power train system, which is the cause of indoor muffled noise. Further, by providing the outer cylinder, that is, the cylindrical elastic bushing at the end of the suspension member, vibration reduction can be further improved.
実施例
以下、本発明の実施例を図に基づいて詳細に説
明する。Embodiments Hereinafter, embodiments of the present invention will be described in detail based on the drawings.
第1図、第2図は本発明の一実施例を示す筒状
弾性ブツシユとしてのマウントインシユレータ1
で、該マウントインシユレータ1で自動車の車体
にサスペンシヨンメンバを結合するようになつて
いる。 1 and 2 show a mount insulator 1 as a cylindrical elastic bushing showing an embodiment of the present invention.
The mount insulator 1 is used to connect a suspension member to the body of an automobile.
即ち、前記マウントインシユレータ1は同心状
に設けられる内筒2および外筒3を有し、これら
内、外筒2,3は加硫接着によつて固着されるゴ
ム製の主弾性体4によつて連結されている。該主
弾性体4は略車両左右方向(第1図中左右方向)
に延び、車両前後方向(第1図中上下方向)の
内、外筒2,3間には空間部5,5aが形成され
ている。尚、前記主弾性体4内には中間板6が設
けられている。 That is, the mount insulator 1 has an inner cylinder 2 and an outer cylinder 3 that are provided concentrically, and the inner and outer cylinders 2 and 3 are attached to a main elastic body 4 made of rubber which is fixed by vulcanization adhesive. connected by. The main elastic body 4 extends substantially in the left-right direction of the vehicle (left-right direction in FIG. 1).
Space portions 5 and 5a are formed between the outer cylinders 2 and 3 in the vehicle longitudinal direction (vertical direction in FIG. 1). Note that an intermediate plate 6 is provided within the main elastic body 4.
ここで、本実施例にあつては前記空間部5,5
aのスペースを利用して、前記外筒3の対向する
内側に、副弾性体7,7aを介して車体側への取
付軸中心つまり内筒2中心に対して対称に配置さ
れる一対の質量体8,8aを加硫接着により固着
してある。該質量体8,8aの内方端部は内筒2
から隔離されて自由端となつており、かつ、前記
主弾性体4にも接触することなく自由に振動する
ことができるようになつている。また、前記副弾
性体7,7aは車両上下方向に剪断変形されるよ
うになつている。尚、前記質量体8,8aは質量
の大きなもの(後述のダイナミツクダンパ機能を
呈することができる大きさ)であれば材質は問わ
ないが、副弾性体7との接着性が良い材質が良好
である。 Here, in this embodiment, the space portions 5, 5
A pair of masses are arranged symmetrically with respect to the center of the axis of attachment to the vehicle body, that is, the center of the inner cylinder 2, via the auxiliary elastic bodies 7, 7a, on the opposing inner sides of the outer cylinder 3, using the space a. The bodies 8, 8a are fixed by vulcanization adhesive. The inner ends of the mass bodies 8, 8a are connected to the inner cylinder 2.
It is isolated from the main elastic body 4 and becomes a free end, and can vibrate freely without coming into contact with the main elastic body 4. Further, the auxiliary elastic bodies 7, 7a are adapted to be sheared and deformed in the vehicle vertical direction. The mass bodies 8 and 8a may be made of any material as long as they have a large mass (a size that allows them to function as a dynamic damper, which will be described later), but materials that have good adhesion to the secondary elastic body 7 are preferred. It is.
そして、以上のように構成されたマウントイン
シユレータ1は、第3図に示すような懸架装置の
サスペンシヨンメンバ10に外筒3が装着され
る。該サスペンシヨンメンバ10は車両左右方向
に延び、前記マウントインシユレータ1はサスペ
ンシヨンメンバ10の車両中心線を対称軸とした
両端部位に夫々対称に装着される。尚、この第3
図はサスペンシヨンメンバ10の片側を示す部分
図で、11は図外の片側のサスペンシヨンアーム
を取着するアームブラケツトである。また、前記
マウントインシユレータ1の内筒2は、この内筒
2内に挿通される図外のボルトを介して図外の車
体に装着される。よつて、前記サスペンシヨンメ
ンバ10はマウントインシユレータ1を介して車
体に結合され、該サスペンシヨンメンバ10の変
位を、マウントインシユレータ1の主弾性体4が
曲げ変形(車両前後方向変位)又は圧縮変形(車
両左右方向変位)されることにより規制すると共
に、前記サスペンシヨンメンバ10に伝達される
路面からの振動が車体側に伝達されるのを抑制す
るようにしてある。 In the mount insulator 1 configured as described above, the outer cylinder 3 is attached to the suspension member 10 of a suspension system as shown in FIG. The suspension member 10 extends in the left-right direction of the vehicle, and the mount insulators 1 are mounted symmetrically at both end portions of the suspension member 10 with the vehicle centerline as an axis of symmetry. Furthermore, this third
The figure is a partial view showing one side of the suspension member 10, and 11 is an arm bracket to which a suspension arm on one side (not shown) is attached. Further, the inner cylinder 2 of the mount insulator 1 is attached to a vehicle body (not shown) via a bolt (not shown) inserted into the inner cylinder 2. Therefore, the suspension member 10 is coupled to the vehicle body via the mount insulator 1, and the main elastic body 4 of the mount insulator 1 bends and deforms the displacement of the suspension member 10 (displacement in the longitudinal direction of the vehicle). Alternatively, the suspension member 10 is compressed and deformed (displaced in the left-right direction of the vehicle), thereby suppressing vibrations from the road surface that are transmitted to the suspension member 10 from being transmitted to the vehicle body.
ところで、本実施例のマウントインシユレータ
1は外筒3に副弾性体7,7aを介して質量体
8,8aが装着されているので、外筒3の振動が
質量体8,8aに伝達されたときには特定周波数
域の振動の位相が180゜ずれて逆位相となり、こ
こにダイナミツクダンパが構成される。つまり、
前記外筒3に特定周波数域の振動が伝達されたと
きには、前記質量体8,8aが逆位相をもつて振
動し、前記外筒3の振動を相殺して該外筒3から
内筒2つまり車体側に伝達される振動を著しく低
減することができるものである。従つて、前記質
量体8,8aの質量を調節する等してダイナミツ
クダンパ効果を発揮する振動周波数域を、従来の
主弾性体では抑制しきれなかつた周波数域に設定
することによつて懸架装置側から車体側に伝達さ
れる路面振動を著しく低減することができる。ま
た、副弾性体7,7aが車両上下方向に剪断変形
されるようになつているので、室内こもり音の原
因となるパワートレイン系の上下振動に対して、
副弾性体7,7aのばね定数を小さくでき、ダイ
ナミツクダンパの共振周波数を特に室内こもり音
の原因となるパワートレイン系の低周波の上下振
動周波数にチユーニングすることができる。この
ため、前記パワートレイン系の振動を効果的に低
減し、こもり音防止を行なうことができるように
なる。 By the way, in the mount insulator 1 of this embodiment, the mass bodies 8, 8a are attached to the outer cylinder 3 via the auxiliary elastic bodies 7, 7a, so the vibration of the outer cylinder 3 is transmitted to the mass bodies 8, 8a. When this happens, the phase of the vibration in the specific frequency range shifts by 180 degrees and becomes the opposite phase, forming a dynamic damper. In other words,
When vibrations in a specific frequency range are transmitted to the outer cylinder 3, the mass bodies 8 and 8a vibrate with opposite phases, canceling out the vibrations of the outer cylinder 3 and causing the outer cylinder 3 to move from the inner cylinder 2. This can significantly reduce vibrations transmitted to the vehicle body. Therefore, by adjusting the mass of the mass bodies 8, 8a, etc., the vibration frequency range in which the dynamic damper effect is exerted is set to a frequency range that cannot be suppressed completely by the conventional main elastic body. Road surface vibrations transmitted from the device side to the vehicle body side can be significantly reduced. In addition, since the secondary elastic bodies 7 and 7a are designed to be sheared in the vertical direction of the vehicle, they are able to withstand vertical vibrations in the powertrain system that cause interior muffled noise.
The spring constants of the auxiliary elastic bodies 7, 7a can be made small, and the resonant frequency of the dynamic damper can be tuned to the low frequency vertical vibration frequency of the power train system, which causes muffled noise in the room. Therefore, vibrations in the power train system can be effectively reduced and muffled noise can be prevented.
ところで、本実施例にあつては、マウントイン
シユレータ1をサスペンシヨンメンバ10の両端
に装着してあるので該サスペンシヨンメンバ10
に作用する曲げ1次共振により車体側に入力され
る荷重を効果的に低減させることができる。 By the way, in this embodiment, since the mount insulator 1 is attached to both ends of the suspension member 10, the suspension member 10
It is possible to effectively reduce the load input to the vehicle body due to the primary bending resonance that acts on the vehicle body.
第4図、第5図はダイナミツクダンパを構成す
る質量体8,8aの質量を変化させた場合と、該
質量体8,8aを一定(1Kg)にしてマウントイ
ンシユレータ1のサスペンシヨンメンバ10の両
端からの取付位置を変化させた場合の夫々の振動
低減効果の比較を計算値によつて示す特性図A,
Bを示す。即ち、これら特性図A,Bにより、本
実施例のマウントインシユレータ1、つまり、質
量体8,8aを空間部5,5a内に配置したダイ
ナミツクダンパ内蔵型のマウントインシユレータ
1にあつても、サスペンシヨンメンバ10の両端
部に取付けることにより、無駄なスペースを有効
的に利用すると共に小さな質量体8,8aにもか
かわらず十分な効果を発揮することができること
が明らかである。 Figures 4 and 5 show the suspension member of the mount insulator 1 when the mass of the mass bodies 8, 8a constituting the dynamic damper is changed, and when the mass bodies 8, 8a are kept constant (1 kg). Characteristic diagram A shows a comparison of vibration reduction effects using calculated values when changing the mounting position from both ends of 10.
Indicates B. That is, based on these characteristic diagrams A and B, the mount insulator 1 of this embodiment, that is, the mount insulator 1 with a built-in dynamic damper in which the mass bodies 8 and 8a are disposed within the spaces 5 and 5a, is suitable. However, it is clear that by attaching the suspension member 10 to both ends of the suspension member 10, wasted space can be used effectively and a sufficient effect can be exerted despite the small mass bodies 8, 8a.
また、サスペンシヨンメンバ10の曲げ1次共
振時の振動方向(第2図中X方向)を吸振しよう
とする場合、それぞれのダイナミツクダンパは前
記振動方向に対する吸振以外に、マウントインシ
ユレータ1に対して以下の2つのモーメントを与
える。即ち、振動方向の質量体8,8aの慣性中
心と取付ゴムの弾性中心とのずれにより発生する
質量体8,8aの回転運動に起因するモーメント
およびサスペンシヨンメンバ10の取付軸中心と
質量体8,8aの慣性中心とのずれに起因するモ
ーメントが生ずる。しかし、本実施例にあつて
は、夫々の質量体8,8aをサスペンシヨンメン
バ10の取付軸中心に対して対称に配置すること
により、前記2つのモーメントは相殺され、効果
的に吸振することが可能となるのである。 In addition, when attempting to absorb vibration in the vibration direction (X direction in FIG. 2) of the suspension member 10 during the primary bending resonance, each dynamic damper is used to absorb vibration in the mount insulator 1 in addition to absorbing vibration in the vibration direction. The following two moments are given to That is, the moment due to the rotational movement of the mass bodies 8, 8a caused by the deviation between the centers of inertia of the mass bodies 8, 8a in the vibration direction and the elastic center of the mounting rubber, and the moment between the center of the mounting shaft of the suspension member 10 and the mass body 8. , 8a arises due to the deviation from the center of inertia. However, in this embodiment, by arranging the respective mass bodies 8 and 8a symmetrically with respect to the center of the mounting axis of the suspension member 10, the two moments are canceled out and vibrations can be effectively absorbed. becomes possible.
更に、前記実施例にあつては夫々の質量体8,
8aで構成されるダイナミツクダンパの吸振周波
数を同一としたものを示したが、これに限ること
なく、夫々のダイナミツクダンパに発生するモー
メントの和があまり大きくならない範囲内で、
夫々のダイナミツクダンパの吸振周波数を違える
こともでき、このようにすることによつて、より
広い周波数域に対して吸振効果を発揮することが
できる。 Furthermore, in the embodiment, each of the mass bodies 8,
Although the vibration absorption frequencies of the dynamic dampers 8a are shown as being the same, the vibration absorption frequency is not limited to this, and as long as the sum of the moments generated in each dynamic damper does not become too large,
The vibration absorption frequency of each dynamic damper can be made different, and by doing so, the vibration absorption effect can be exerted over a wider frequency range.
尚、本考案は一般に用いられるセミトレーリン
グタイプのサスペンシヨンメンバに限ることな
く、他のサスペンシヨンたとえばマルチリンクタ
イプのものにあつても適用することができること
はいうまでもない。 It goes without saying that the present invention is not limited to the commonly used semi-trailing type suspension member, but can also be applied to other suspensions, such as multi-link types.
発明の効果
以上説明したように本発明のサスペンシヨンメ
ンバの筒状弾性ブツシユにあつては、サスペンシ
ヨンメンバに装着される外筒に、副弾性体を介し
て質量体を装着したので、これら副弾性体、質量
体によつて該質量体を装着した筒体に対してダイ
ナミツクダンパが構成され、該筒体に伝達される
特定周波数域の振動を低減することができる。特
に、前記副弾性体は車両上下方向に剪断変形され
るように配置したので、パワートレイン系の上下
振動に対するダイナミツクダンパの共振周波数を
特に室内こもり音の原因となるパワートレイン系
の低周波の上下振動周波数にチユーニングするこ
とができ、室内こもり音の防止著しくは大幅な低
減を行なうことができる。更に、弾性ブツシユを
サスペンシヨンメンバの端部に設けたので、振動
低減効果を更に向上することができる。従つて、
この振動低減される周波数域を、前記内、外筒を
連結し、緩衝機能および変位規制機能を備えた主
弾性体で抑制しきれない振動周波数域に設定する
ことによつて、振動体制から基本側に伝達される
振動を、変位規制機能を満足しつつ著しく低減さ
せることができるという優れた効果を奏する。Effects of the Invention As explained above, in the cylindrical elastic bushing of the suspension member of the present invention, the mass body is attached to the outer cylinder attached to the suspension member via the auxiliary elastic body. The elastic body and the mass body constitute a dynamic damper for the cylindrical body to which the mass body is attached, and can reduce vibrations in a specific frequency range transmitted to the cylindrical body. In particular, since the secondary elastic body is arranged so as to be sheared in the vertical direction of the vehicle, the resonant frequency of the dynamic damper against the vertical vibration of the powertrain system can be reduced, especially the low frequency of the powertrain system that causes indoor muffled noise. It is possible to tune the vertical vibration frequency, and it is possible to prevent and significantly reduce indoor muffled noise. Furthermore, since the elastic bushing is provided at the end of the suspension member, the vibration reduction effect can be further improved. Therefore,
By setting the frequency range in which this vibration is reduced to a vibration frequency range that cannot be suppressed by the main elastic body that connects the inner and outer cylinders and has a buffering function and a displacement regulating function, the basic vibration system can be reduced. This provides an excellent effect in that vibrations transmitted to the sides can be significantly reduced while satisfying the displacement regulation function.
第1図は本発明の一実施例を示す筒状弾性ブツ
シユの横断面図、第2図は第1図中−線矢視
断面図、第3図はサスペンシヨンメンバへの筒状
弾性ブツシユの取付状態を示す要部平面図、第4
図はダイナミツクダンパの質量に対する振動低減
状態を示す特性図、第5図は筒状弾性ブツシユの
取付位置に対する振動低減状態を示す特性図であ
る。
1……マウントインシユレータ(筒状弾性ブツ
シユ)、2……内筒、3……外筒、4……主弾性
体、7……副弾性体、8……質量体、10……サ
スペンシヨンメンバ。
FIG. 1 is a cross-sectional view of a cylindrical elastic bushing showing an embodiment of the present invention, FIG. 2 is a cross-sectional view taken along the line - 1 in FIG. Main part plan view showing the installation state, No. 4
This figure is a characteristic diagram showing the vibration reduction state with respect to the mass of the dynamic damper, and FIG. 5 is a characteristic diagram showing the vibration reduction state with respect to the mounting position of the cylindrical elastic bushing. 1...Mount insulator (cylindrical elastic bush), 2...Inner tube, 3...Outer tube, 4...Main elastic body, 7...Sub-elastic body, 8...Mass body, 10...Suspension Shion member.
Claims (1)
ンバ側に装着される外筒およびこれら内、外筒を
連結する主弾性体からなり、前記サスペンシヨン
メンバを車体に支持させるようにしたサスペンシ
ヨンメンバの筒状弾性ブツシユにおいて、前記外
筒をサスペンシヨンメンバの端部に配置すると共
に、該外筒の内側に車両上下方向に剪断変形する
副弾性体を介してダイナミツクダンパ機能を行な
うに十分な質量を有する質量体を装着したことを
特徴とするサスペンシヨンメンバの筒状弾性ブツ
シユ。 2 前記質量体が内筒の軸中心に対して対称に配
設されていることを特徴とする特許請求の範囲第
1項に記載のサスペンシヨンメンバの筒状弾性ブ
ツシユ。[Claims] 1. Consisting of an inner cylinder mounted on the vehicle body side, an outer cylinder mounted on the suspension member side, and a main elastic body connecting these inner and outer cylinders, the suspension member is supported by the vehicle body. In the cylindrical elastic bushing of the suspension member, the outer cylinder is disposed at the end of the suspension member, and a dynamic damper is installed inside the outer cylinder via an auxiliary elastic body that is sheared in the vertical direction of the vehicle. A cylindrical elastic bushing for a suspension member, characterized in that it is equipped with a mass body having a mass sufficient to perform its functions. 2. The cylindrical elastic bushing for a suspension member according to claim 1, wherein the mass body is arranged symmetrically with respect to the axial center of the inner cylinder.
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP58122980A JPS6014627A (en) | 1983-07-06 | 1983-07-06 | Sleeve-like elastic bush |
US06/619,482 US4889328A (en) | 1983-07-06 | 1984-06-11 | Insulator for use in automotive suspension or the like |
EP84107341A EP0131795B1 (en) | 1983-07-06 | 1984-06-26 | Improved insulator for use in automotive suspension or the like |
DE8484107341T DE3479916D1 (en) | 1983-07-06 | 1984-06-26 | Improved insulator for use in automotive suspension or the like |
US07/370,787 US4951930A (en) | 1983-07-06 | 1989-06-23 | Insulator for use in automotive suspension or the like |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP58122980A JPS6014627A (en) | 1983-07-06 | 1983-07-06 | Sleeve-like elastic bush |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS6014627A JPS6014627A (en) | 1985-01-25 |
JPS6216335B2 true JPS6216335B2 (en) | 1987-04-11 |
Family
ID=14849326
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP58122980A Granted JPS6014627A (en) | 1983-07-06 | 1983-07-06 | Sleeve-like elastic bush |
Country Status (4)
Country | Link |
---|---|
US (2) | US4889328A (en) |
EP (1) | EP0131795B1 (en) |
JP (1) | JPS6014627A (en) |
DE (1) | DE3479916D1 (en) |
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-
1984
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- 1984-06-26 EP EP84107341A patent/EP0131795B1/en not_active Expired
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-
1989
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Also Published As
Publication number | Publication date |
---|---|
DE3479916D1 (en) | 1989-11-02 |
US4951930A (en) | 1990-08-28 |
EP0131795A3 (en) | 1987-02-04 |
US4889328A (en) | 1989-12-26 |
EP0131795A2 (en) | 1985-01-23 |
EP0131795B1 (en) | 1989-09-27 |
JPS6014627A (en) | 1985-01-25 |
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